JP5182474B2 - Integrated piston piston - Google Patents

Integrated piston piston Download PDF

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JP5182474B2
JP5182474B2 JP2007209354A JP2007209354A JP5182474B2 JP 5182474 B2 JP5182474 B2 JP 5182474B2 JP 2007209354 A JP2007209354 A JP 2007209354A JP 2007209354 A JP2007209354 A JP 2007209354A JP 5182474 B2 JP5182474 B2 JP 5182474B2
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outer peripheral
piston
clutch
seal
cylindrical portion
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JP2009041709A (en
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智昭 西村
宏治 藤井
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Nok Corp
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Nok Corp
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Priority to US12/187,711 priority patent/US20090038906A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/005—Pistons; Trunk pistons; Plungers obtained by assembling several pieces
    • F16J1/006—Pistons; Trunk pistons; Plungers obtained by assembling several pieces of different materials
    • F16J1/008—Pistons; Trunk pistons; Plungers obtained by assembling several pieces of different materials with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0212—Details of pistons for master or slave cylinders especially adapted for fluid control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Description

本発明は、車両の自動変速機の油圧作動クラッチに用いられるシール一体型ピストンに関する。   The present invention relates to a seal-integrated piston used for a hydraulically operated clutch of an automatic transmission of a vehicle.

車両の自動変速機における油圧作動クラッチは、油圧によってクラッチシリンダ内を軸方向移動するクラッチピストンが、多板クラッチにおける駆動軸側のドライブプレートと従動軸側のドリブンプレートとを圧接させるようになっており、前記クラッチピストンとしては、ピストン本体の外周部及び内周部にシールリップが加硫接着によって一体化されたシール一体型ピストン（ボンデッドピストンシール又はシールボンデッドピストンとも呼ばれる）が知られている。   In a hydraulically operated clutch in an automatic transmission of a vehicle, a clutch piston that moves axially in a clutch cylinder by hydraulic pressure presses a drive plate on a drive shaft side and a driven plate on a driven shaft side in a multi-plate clutch. As the clutch piston, a seal-integrated piston (also called a bonded piston seal or a seal bonded piston) in which a seal lip is integrated by vulcanization adhesion on the outer peripheral portion and the inner peripheral portion of the piston body is known. Yes.

図４は、従来のシール一体型ピストンを用いた油圧作動クラッチの概略構成を、軸心Ｏを通る平面で切断して示す片側断面図、図５は、図４の一部を拡大した断面図である。図４に示される油圧作動クラッチにおいて、参照符号１は、不図示の駆動軸と共に回転する環状のクラッチシリンダ、２は、クラッチシリンダ１内に軸方向移動可能に配置され、このクラッチシリンダ１の端盤部１ａとの間に油圧室４を画成するシール一体型ピストン、３は、クラッチシリンダ１に軸方向移動可能な状態で円周方向に係止された複数のドライブプレート３１と、不図示の従動軸側に設けられたクラッチハブ３３に軸方向移動可能な状態で円周方向に係止された複数のドリブンプレート３２が軸方向交互に配置された多板クラッチである。クラッチシリンダ１の内筒部１ｃには、油圧室４にオイル（ＡＴＦ）による油圧を導入するための油通路１ｄが開設されている。 Figure 4 is a schematic configuration of a hydraulic clutch using the conventional seal-integrated piston, half sectional view taken in a plane passing through an axis O, FIG. 5 is a sectional view showing an enlarged portion of FIG. 4 It is. In the hydraulically operated clutch shown in FIG. 4 , reference numeral 1 is an annular clutch cylinder that rotates together with a drive shaft (not shown), and 2 is disposed in the clutch cylinder 1 so as to be axially movable. A seal-integrated piston 3 that defines a hydraulic chamber 4 between the disk portion 1a and a plurality of drive plates 31 that are engaged with the clutch cylinder 1 in a circumferential direction so as to be axially movable. This is a multi-plate clutch in which a plurality of driven plates 32 that are locked in the circumferential direction while being axially movable to a clutch hub 33 provided on the driven shaft side are alternately arranged in the axial direction. In the inner cylinder portion 1 c of the clutch cylinder 1, an oil passage 1 d for introducing hydraulic pressure by oil (ATF) into the hydraulic chamber 4 is opened.

シール一体型ピストン２は、金属プレス成形品のピストン本体２１と、その内外周に一体的に成形されて、クラッチシリンダ１の外筒部１ｂ及び内筒部１ｃと摺動可能に密接されたゴム状弾性材料からなるシールリップ２２，２３を一体に有し、不図示のリターンスプリングによって、油圧室４の容積を縮小する方向、言い換えれば多板クラッチ３から遠ざかる方向へ付勢されている。ピストン本体２１の外周筒部２１ａは、その先端がクラッチ押圧部２１ｂとなっていて、多板クラッチ３と軸方向に対向している。   The seal-integrated piston 2 is a rubber body that is integrally formed on the inner and outer periphery of a piston body 21 that is a metal press-molded product, and is slidably intimately contacted with the outer cylinder portion 1b and the inner cylinder portion 1c of the clutch cylinder 1. The seal lips 22, 23 made of an elastic material are integrally formed, and are urged by a return spring (not shown) in a direction to reduce the volume of the hydraulic chamber 4, in other words, away from the multi-plate clutch 3. The distal end of the outer peripheral cylindrical portion 21a of the piston body 21 is a clutch pressing portion 21b, and is opposed to the multi-plate clutch 3 in the axial direction.

すなわちこの油圧作動クラッチは、油通路１ｄを介して油圧室４に油圧を印加することによって、シール一体型ピストン２が不図示のリターンスプリングの付勢力に抗してクラッチシリンダ１内を軸方向変位し、多板クラッチ３におけるドライブプレート３１をドリブンプレート３２に押し付けるので、駆動軸から従動軸へ動力を伝達する接続状態となる。   That is, this hydraulically operated clutch applies an oil pressure to the hydraulic chamber 4 through the oil passage 1d, so that the seal-integrated piston 2 is axially displaced in the clutch cylinder 1 against the biasing force of a return spring (not shown). Then, since the drive plate 31 in the multi-plate clutch 3 is pressed against the driven plate 32, a connection state is established in which power is transmitted from the drive shaft to the driven shaft.

次に、油圧室４の油圧を開放すると、シール一体型ピストン２は、リターンスプリングの付勢力によって、油圧室４の容積を縮小させる方向へクラッチシリンダ１内を軸方向変位して、多板クラッチ３におけるドライブプレート３１とドリブンプレート３２の圧接を解除するので、駆動軸から従動軸への動力伝達を遮断する（例えば、下記の特許文献１参照）。
特開２００１−２４１４６７号公報 Next, when the hydraulic pressure in the hydraulic chamber 4 is released, the seal-integrated piston 2 is axially displaced in the clutch cylinder 1 in a direction to reduce the volume of the hydraulic chamber 4 by the biasing force of the return spring, so that the multi-plate clutch 3 is released, the power transmission from the drive shaft to the driven shaft is interrupted (see, for example, Patent Document 1 below).
JP 2001-241467 A

この種の油圧作動クラッチのシール一体型ピストン２は、外周側のシールリップ２２をピストン本体２１に一体成形する際に、成形用ゴム材料の流れをピストン本体２１の外周筒部２１ａの外周面で止めることが困難であるため、外周側のシールリップ２２からは、ピストン本体２１の外周筒部２１ａの外周面を被覆するように延びるゴム膜２２ａが形成されている。そして、このゴム膜２２ａの先端がクラッチ押圧部２１ｂに廻り込んでいるようなことがあると、多板クラッチ３との接触の際に、クラッチ押圧部２１ｂのゴムが剥離することによるコンタミを発生してしまうため、従来は、図５に示されるように、クラッチ押圧部２１ｂの外周側に、軸心とほぼ直交する平面をなす環状段差部２１ｃを凹設し、この環状段差部２１ｃにおいて、成形時のゴム止めを行うようにしている。 In this type of hydraulically-actuated clutch-integrated piston 2, when the outer peripheral seal lip 22 is integrally formed with the piston body 21, the flow of the molding rubber material is changed on the outer peripheral surface of the outer peripheral cylindrical portion 21 a of the piston body 21. Since it is difficult to stop, a rubber film 22a extending from the outer peripheral seal lip 22 so as to cover the outer peripheral surface of the outer peripheral cylindrical portion 21a of the piston main body 21 is formed. If the tip of the rubber film 22a wraps around the clutch pressing portion 21b, contamination due to peeling of the rubber of the clutch pressing portion 21b is generated when contacting the multi-plate clutch 3. Therefore, conventionally, as shown in FIG. 5 , an annular stepped portion 21c having a plane substantially orthogonal to the axial center is provided on the outer peripheral side of the clutch pressing portion 21b. The rubber stopper is used at the time of molding.

ところがこの場合、環状段差部２１ｃに金型を押し付けてゴムの廻り込みを確実に遮断するため、環状段差部２１ｃの径方向幅ｗ１を所定の大きさ以上に形成する必要がある。このため、クラッチ押圧部２１ｂの幅（押圧面積）ｗ２が狭くなり、多板クラッチ３を押圧する際のクラッチ押圧部２１ｂの面圧が大きくなって摩耗が進行しやすく、またこれにより、多板クラッチ３との距離が変化して変速機の機能に悪影響を及ぼす懸念があった。 However, in this case, it is necessary to form the radial width w 1 of the annular step portion 21c to be equal to or larger than a predetermined size in order to reliably block the rubber from entering by pressing the mold against the annular step portion 21c. Therefore, narrows the clutch width of the pressing portion 21b (pressing area) w 2, multi-plate clutch 3 wear surface pressure is increased in the clutch pressing portion 21b at the time of pressing it is likely to proceed, and thereby, a multi There is a concern that the distance from the plate clutch 3 may change and adversely affect the transmission function.

本発明は、以上のような点に鑑みてなされたものであって、その技術的課題とするところは、油圧作動クラッチに用いられるシール一体型ピストンにおいて、クラッチ押圧部の極力大きな押圧面積を確保することにある。   The present invention has been made in view of the above points, and the technical problem thereof is to ensure a large pressing area of the clutch pressing portion in the seal-integrated piston used in the hydraulically operated clutch. There is to do.

上述した技術的課題を有効に解決するための手段として、請求項１の発明に係るシール一体型ピストンは、クラッチシリンダ内に軸方向移動可能に配置されたピストン本体と、このピストン本体の外周筒部に一体に設けられ前記クラッチシリンダの内面に軸方向摺動可能に密接されるシールリップとを備え、前記ピストン本体の外周筒部の外周面に先端側へ向けて小径となり前記外周筒部の肉厚を減少させる円錐状段差面が形成され、前記ピストン本体の外周筒部の先端に、多板クラッチを押圧可能なクラッチ押圧部が前記円錐状段差面を介して突設され、前記シールリップの基部から前記ピストン本体の外周筒部の外周面を覆うように延びるゴム膜の端部が、前記円錐状段差面又はこの円錐状段差面の端部に位置することを特徴としている。すなわち、ピストン本体の外周筒部にシールリップを一体成形する際のゴム止めを前記円錐状段差面で行うことによって、ピストン本体の外周筒部の径方向幅におけるクラッチ押圧部の大きな径方向幅を確保したものである。 As means for effectively solving the above technical problem, a seal-integrated piston according to the invention of claim 1 includes a piston main body disposed in a clutch cylinder so as to be axially movable, and an outer peripheral cylinder of the piston main body. A seal lip provided integrally with the inner surface of the clutch cylinder so as to be slidable in the axial direction. The outer peripheral surface of the outer peripheral cylindrical portion of the piston body has a small diameter toward the distal end, and the outer peripheral cylindrical portion A conical step surface for reducing the thickness is formed, and a clutch pressing portion capable of pressing a multi-plate clutch is provided at the tip of the outer peripheral cylindrical portion of the piston body through the conical step surface, and the seal lip The end portion of the rubber film extending from the base portion so as to cover the outer peripheral surface of the outer peripheral cylindrical portion of the piston body is located at the conical step surface or the end portion of the conical step surface. In other words, by carrying out the rubber stopper when the seal lip is integrally formed on the outer peripheral cylindrical portion of the piston main body with the conical step surface, the large radial width of the clutch pressing portion in the radial width of the outer peripheral cylindrical portion of the piston main body is increased. Secured.

請求項１の発明に係るシール一体型ピストンによれば、シールリップを一体成形する際のゴム止めを、ピストン本体の外周筒部に形成した円錐状段差面で行うことによって、径方向幅が十分に大きなクラッチ押圧部を確保することができ、その結果、多板クラッチを押圧する際のクラッチ押圧部の面圧を低下させて摩耗を抑えることができるので、変速機への悪影響を防止することができる。 According to the seal-integrated piston according to the first aspect of the invention, the radial width is sufficient by performing the rubber stopper when integrally forming the seal lip with the conical step surface formed in the outer peripheral cylindrical portion of the piston body. A large clutch pressing portion can be secured, and as a result, the surface pressure of the clutch pressing portion when pressing the multi-plate clutch can be reduced to suppress wear, thereby preventing adverse effects on the transmission. Can do.

以下、本発明に係るシール一体型ピストンの好ましい実施の形態について、図面を参照しながら説明する。図１は、本発明に係るシール一体型ピストンの第一の形態を、油圧作動クラッチの一部と共に軸心Ｏを通る平面で切断して示す片側断面図、図２は、図１の要部拡大断面図である。   Hereinafter, preferred embodiments of a seal-integrated piston according to the present invention will be described with reference to the drawings. FIG. 1 is a half sectional view showing a first embodiment of a piston with an integrated seal according to the present invention by cutting along a plane passing through an axis O together with a part of a hydraulically operated clutch, and FIG. 2 is a main portion of FIG. It is an expanded sectional view.

図１に示される自動変速機用油圧作動クラッチにおいて、参照符号１１０は、不図示の駆動軸と共に軸心Ｏの周りに回転されるクラッチシリンダ、参照符号１２０は、クラッチシリンダ１１０内に軸方向移動可能に配置された、本発明に係るシール一体型ピストン、参照符号１３０は、多板クラッチである。   In the hydraulically operated clutch for an automatic transmission shown in FIG. 1, reference numeral 110 is a clutch cylinder rotated around an axis O together with a drive shaft (not shown), and reference numeral 120 is moved in the axial direction into the clutch cylinder 110. The seal-integrated piston according to the present invention, which is arranged in a possible manner, is a multi-plate clutch.

クラッチシリンダ１１０は、外周部材１１１と内周部材１１２の接合体であって、外周部材１１１は、内向き鍔部１１１ａと、その外周側の円錐壁部１１１ｂと、その外周端から外周側へ展開した円盤部１１１ｃと、さらにその外周端から前記円錐壁部１１１ｂと同心に折り返されるように形成された外筒部１１１ｄからなり、内周部材１１２は、外周縁が外周部材１１１の内向き鍔部１１１ａと密接嵌合した状態で一体に接合された外向き鍔部１１２ａと、その内周端から外周部材１１１の外筒部１１１ｄと同心に延びる内筒部１１２ｂとを備える。   The clutch cylinder 110 is a joined body of the outer peripheral member 111 and the inner peripheral member 112, and the outer peripheral member 111 expands from the outer peripheral end to the outer peripheral side from the inward flange portion 111a, the outer peripheral conical wall portion 111b. Disk portion 111c, and outer cylindrical portion 111d formed so as to be folded concentrically with conical wall portion 111b from the outer peripheral end thereof, and inner peripheral member 112 has an outer peripheral edge that is an inward flange portion of outer peripheral member 111. The outer flange portion 112a is integrally joined in a state of being closely fitted to 111a, and the inner cylinder portion 112b extending concentrically with the outer cylinder portion 111d of the outer circumferential member 111 from the inner circumferential end thereof.

多板クラッチ１３０は、クラッチシリンダ１１０の外筒部１１１ｄに軸方向移動可能な状態で円周方向に係止された複数のドライブプレート１３１と、不図示の従動軸側に設けられたクラッチハブ１３３に軸方向移動可能な状態で円周方向に係止された複数のドリブンプレート１３２が軸方向交互に配置された構造を備える。   The multi-plate clutch 130 includes a plurality of drive plates 131 that are locked in the circumferential direction so as to be axially movable on the outer cylinder portion 111d of the clutch cylinder 110, and a clutch hub 133 that is provided on the driven shaft side (not shown). A plurality of driven plates 132 locked in the circumferential direction so as to be axially movable are arranged alternately in the axial direction.

本発明の第一の形態に係るシール一体型ピストン１２０は、軸心Ｏを中心とする環状を呈するピストン本体１２１と、このピストン本体１２１に一体に設けられたシールリップ１２２，１２３とを備える。   The seal-integrated piston 120 according to the first embodiment of the present invention includes a piston main body 121 having an annular shape centering on an axis O, and seal lips 122 and 123 provided integrally with the piston main body 121.

シール一体型ピストン１２０におけるピストン本体１２１は、金属板のプレス成形によって製作されたものであって、クラッチシリンダ１１０における外周部材１１１の円盤部１１１ｃと対向される円盤状の外周側受圧部１２１ａと、前記外周部材１１１の円錐壁部１１１ｂと対向される円錐状の中間受圧部１２１ｂと、前記外周部材１１１の内向き鍔部１１１ａ及び内周部材１１２の外向き鍔部１１２ａと対向される円盤状の内周側受圧部１２１ｃと、さらにその内周側に形成された内周屈曲端部１２１ｄと、前記外周側受圧部１２１ａの外周端から折り返されて、前記外周部材１１１の外筒部１１１ｄと径方向に対向される外周筒部１２１ｅと、さらに、この外周筒部１２１ｅの外周面に先端側へ向けて小径となるように形成された円錐状段差面１２１ｇを介して、前記外周筒部１２１ｅの先端に突設されたクラッチ押圧部１２１ｆとを備える。   The piston main body 121 in the seal-integrated piston 120 is manufactured by press-molding a metal plate, and a disk-shaped outer peripheral pressure receiving portion 121a facing the disk portion 111c of the outer peripheral member 111 in the clutch cylinder 110; A conical intermediate pressure receiving portion 121b opposed to the conical wall portion 111b of the outer peripheral member 111, a disc-like shape opposed to the inward flange portion 111a of the outer peripheral member 111 and the outward flange portion 112a of the inner peripheral member 112. The inner circumferential pressure receiving portion 121c, the inner circumferential bent end portion 121d formed on the inner circumferential side thereof, and the outer cylindrical portion 111d of the outer circumferential member 111 and the diameter thereof are folded back from the outer circumferential end of the outer circumferential pressure receiving portion 121a. Outer peripheral cylindrical portion 121e facing in the direction, and a cone formed on the outer peripheral surface of the outer peripheral cylindrical portion 121e so as to have a smaller diameter toward the tip side. Via a step surface 121g, and a clutch pressing portion 121f projecting from the distal end of the outer peripheral tubular portion 121e.

クラッチシリンダ１１０における外周部材１１１の円盤部１１１ｃから内周部材１１２の外向き鍔部１１２ａにかけての部分と、これに対向されるピストン本体１２１の外周側受圧部１２１ａから内周屈曲端部１２１ｄにかけての部分との間には、シールリップ１２２，１２３によって油圧室１４０が画成され、クラッチシリンダ１１０における内周部材１１２の内筒部１１２ｂには、油圧室１４０にオイル（ＡＴＦ）による油圧を導入するための油通路１１２ｃが開設されている。   In the clutch cylinder 110, a portion from the disk portion 111c of the outer peripheral member 111 to the outward flange portion 112a of the inner peripheral member 112, and an outer peripheral pressure receiving portion 121a of the piston main body 121 opposed thereto to the inner peripheral bent end portion 121d. A hydraulic chamber 140 is defined between the portions by the seal lips 122 and 123, and oil pressure by oil (ATF) is introduced into the hydraulic chamber 140 into the inner cylinder portion 112 b of the inner peripheral member 112 in the clutch cylinder 110. An oil passage 112c is opened.

また、ピストン本体１２１の内周側受圧部１２１ｃには、油圧室１４０側へ打ち出された複数の突起１２１ｈが、円周方向等間隔で形成されている。この突起１２１ｈは、ピストン本体１２１がその上死点位置まで移動した時に、クラッチシリンダ１１０における内周部材１１２の外向き鍔部１１２ａと当接し、油圧室１４０が閉塞することのないようにするものである   In addition, a plurality of protrusions 121h that are driven out toward the hydraulic chamber 140 are formed on the inner circumferential pressure receiving portion 121c of the piston main body 121 at equal intervals in the circumferential direction. The protrusion 121h is configured to abut against the outward flange 112a of the inner peripheral member 112 of the clutch cylinder 110 when the piston body 121 moves to its top dead center position, so that the hydraulic chamber 140 is not blocked. Is

シール一体型ピストン１２０におけるシールリップ１２２，１２３は、ピストン本体１２１の外周筒部１２１ｅにおけるクラッチ押圧部１２１ｆと反対側の肩部と、内周屈曲端部１２１ｄの内周面に、ゴム状弾性材料によって一体的に成形されたものである。このうち、外周側のシールリップ１２２は、クラッチシリンダ１１０の外筒部１１１ｄの内周面と摺動可能に密接され、内周側のシールリップ１２３は、クラッチシリンダ１１０の内周筒部１１２ｂの外周面と摺動可能に密接される。   The seal lips 122 and 123 in the seal-integrated piston 120 are provided with rubber-like elastic material on the shoulder portion on the opposite side of the clutch pressing portion 121f in the outer peripheral cylindrical portion 121e of the piston main body 121 and the inner peripheral surface of the inner peripheral bent end portion 121d. It is formed integrally by. Among these, the outer peripheral side seal lip 122 is slidably in close contact with the inner peripheral surface of the outer cylinder part 111 d of the clutch cylinder 110, and the inner peripheral side seal lip 123 is connected to the inner peripheral cylinder part 112 b of the clutch cylinder 110. It is slidably in close contact with the outer peripheral surface.

外周側のシールリップ１２２からは、ピストン本体１２１の外周筒部１２１ｅの外周面を被覆するように延びるゴム膜１２４が形成されている。そして、このゴム膜１２４の先端は、前記外周筒部１２１ｅの外周面に形成された円錐状段差面１２１ｇに位置している。   A rubber film 124 extending from the outer peripheral seal lip 122 so as to cover the outer peripheral surface of the outer peripheral cylindrical portion 121e of the piston main body 121 is formed. And the front-end | tip of this rubber film 124 is located in the conical level | step difference surface 121g formed in the outer peripheral surface of the said outer periphery cylinder part 121e.

一方、内周側のシールリップ１２３からは、ピストン本体１２１の内周屈曲端部１２１ｄの内周面を被覆するように延びるゴム膜１２５が形成されている。そして、このゴム膜１２５の先端は、徐々に薄肉になりながら、前記内周屈曲端部１２１ｄと内周側受圧部１２１ｃとの境界部分まで延びている。   On the other hand, a rubber film 125 extending from the inner peripheral side seal lip 123 so as to cover the inner peripheral surface of the inner peripheral bent end 121d of the piston main body 121 is formed. The tip of the rubber film 125 extends to the boundary portion between the inner peripheral bent end 121d and the inner peripheral pressure receiving portion 121c while gradually becoming thinner.

以上の構成を備える油圧作動クラッチは、先に説明した図４と同様、油通路１１２ｃを介して油圧室１４０へ油圧を印加し、あるいはこの油圧を開放することによって、本発明に係るシール一体型ピストン１２０がクラッチシリンダ１１０内を軸方向に変位して、多板クラッチ１３０を接続動作あるいは遮断動作させるものである。 The hydraulically operated clutch having the above-described configuration is similar to FIG. 4 described above, and applies a hydraulic pressure to the hydraulic chamber 140 via the oil passage 112c or releases the hydraulic pressure, thereby integrating the seal according to the present invention. The piston 120 is displaced in the axial direction in the clutch cylinder 110, and the multi-plate clutch 130 is connected or disconnected.

すなわち、オイル（ＡＴＦ）の供給によって油圧室１４０が加圧されると、シール一体型ピストン１２０が、不図示のリターンスプリングを圧縮させながら、図１における下方へ変位し、このシール一体型ピストン１２０のクラッチ押圧部１２１ｆが、多板クラッチ１３０を押圧して、この多板クラッチ１３０のドライブプレート１３１とドリブンプレート１３２とを摩擦係合させる。このため、多板クラッチ１３０が接続状態となって、不図示の駆動軸側からの駆動トルクが、クラッチシリンダ１１０、多板クラッチ１３０のドライブプレート１３１とドリブンプレート１３２及びクラッチハブ１３３を介して、不図示の従動軸へ伝達される。   That is, when the hydraulic chamber 140 is pressurized by supplying oil (ATF), the seal-integrated piston 120 is displaced downward in FIG. 1 while compressing a return spring (not shown). The clutch pressing portion 121f presses the multi-plate clutch 130 to frictionally engage the drive plate 131 and the driven plate 132 of the multi-plate clutch 130. For this reason, the multi-plate clutch 130 is in a connected state, and drive torque from the drive shaft side (not shown) is transmitted via the clutch cylinder 110, the drive plate 131 and the driven plate 132 of the multi-plate clutch 130, and the clutch hub 133. It is transmitted to a driven shaft (not shown).

また、この接続状態から、油圧室１４０の油圧を開放すると、圧縮されたリターンスプリングの復元（伸長）によって、シール一体型ピストン１２０が、油圧室１４０の容積を縮小させるように図１における上方へ変位し、多板クラッチ１３０への押圧を解除するので、この多板クラッチ１３０のドライブプレート１３１とドリブンプレート１３２の摩擦係合が解除され、駆動軸から従動軸への駆動トルクの伝達が遮断される。   Further, when the hydraulic pressure in the hydraulic chamber 140 is released from this connected state, the seal-integrated piston 120 moves upward in FIG. 1 so that the volume of the hydraulic chamber 140 is reduced by restoring (extending) the compressed return spring. Displacement and release of the pressure on the multi-plate clutch 130 are released, so that the frictional engagement between the drive plate 131 and the driven plate 132 of the multi-plate clutch 130 is released, and transmission of drive torque from the drive shaft to the driven shaft is cut off. The

ここで、ピストン本体１２１の外周筒部１２１ｅの外周面を被覆するように延びるゴム膜１２４は、外周側のシールリップ１２２をピストン本体１２１に一体成形する際に、シールリップ１２２を成形する不図示のキャビティからピストン本体１２１の外周筒部１２１ｅの外周面に沿って流れる成形用ゴム材料によって形成されたものである。そしてこのとき、不図示の金型の内面を、ピストン本体１２１の外周筒部１２１ｅに形成した円錐状段差面１２１ｇに密接させることによって、成形用ゴム材料がクラッチ押圧部１２１ｆの押圧面１２１ｉへ廻り込むことのないようにゴム止めされている。   Here, the rubber film 124 extending so as to cover the outer peripheral surface of the outer peripheral cylindrical portion 121e of the piston main body 121 forms the seal lip 122 when the outer peripheral seal lip 122 is integrally formed with the piston main body 121 (not shown). These are formed by a molding rubber material that flows along the outer peripheral surface of the outer peripheral cylindrical portion 121e of the piston main body 121 from the cavity. At this time, the molding rubber material moves to the pressing surface 121i of the clutch pressing portion 121f by bringing the inner surface of the mold (not shown) into close contact with the conical step surface 121g formed on the outer peripheral cylindrical portion 121e of the piston body 121. Rubberized to prevent it from entering.

詳しくは、図２に示されるように、円錐状段差面１２１ｇは、十分な幅ｗ３を確保することができるので、ここに不図示の金型を密接させることによって、確実にゴム止めを行うことができる。しかも、円錐状段差面１２１ｇの傾斜角度をθとすると、円錐状段差面１２１ｇの径方向幅ｗ１は、
ｗ１＝ｗ３ｓｉｎθ
であり、円錐状段差面１２１ｇの幅ｗ３よりも十分に小さなものとすることができる。したがって、ピストン本体１２１の外周筒部１２１ｅの肉厚ｔに対して、クラッチ押圧部１２１ｆの肉厚（押圧面１２１ｉの径方向幅ｗ２）がそれほど小さくならず、すなわち多板クラッチ１３０に対する比較的大きな押圧面積が確保されるので、クラッチ押圧部１２１ｆの面圧が抑えられ、ひいては押圧面１２１ｉの摩耗の進行を抑えることができる。 Specifically, as shown in FIG. 2, the conical step surface 121g is, it is possible to secure a sufficient width w 3, by close contact with the mold not shown here, to reliably perform rubber stopper be able to. Moreover, when the inclination angle of the conical step surface 121g and theta, radial width w 1 of the conical step surface 121g is
w 1 = w 3 sin θ
, And the can be sufficiently smaller than the width w 3 of the conical step surface 121g. Therefore, the thickness of the clutch pressing portion 121f (the radial width w 2 of the pressing surface 121i) is not so small with respect to the thickness t of the outer peripheral cylindrical portion 121e of the piston main body 121, that is, relatively to the multi-plate clutch 130. Since a large pressing area is secured, the surface pressure of the clutch pressing portion 121f can be suppressed, and as a result, the progress of wear of the pressing surface 121i can be suppressed.

図３は、第一の形態における形状変更例を示す要部拡大断面図である。すなわち、ピストン本体１２１の外周筒部１２１ｅの外周面を被覆するように延びるゴム膜１２４の先端は、図３の（Ａ）に示されるように、金型２００の内面にピストン本体１２１の円錐状段差面１２１ｇと対応して形成した円錐面２０１を密接（面接触）させることによってゴム止めを行ったものでも良く、あるいは図３の（Ｂ）に示されるように、金型２００の内面にピストン本体１２１の円錐状段差面１２１ｇより小さな傾斜角度で形成した円錐面２０２を、ピストン本体１２１の円錐状段差面１２１ｇの肩部と密接（線接触）させることによってゴム止めを行ったものでも良い。   FIG. 3 is an enlarged cross-sectional view of a main part showing a shape change example in the first embodiment. That is, the tip of the rubber film 124 extending so as to cover the outer peripheral surface of the outer peripheral cylindrical portion 121e of the piston main body 121 is conical with the piston main body 121 on the inner surface of the mold 200 as shown in FIG. The conical surface 201 formed to correspond to the stepped surface 121g may be in close contact (surface contact) with a rubber stopper, or, as shown in FIG. The conical surface 202 formed with an inclination angle smaller than the conical step surface 121g of the main body 121 may be rubber-fixed by bringing it into close contact (line contact) with the shoulder of the conical step surface 121g of the piston main body 121.

本発明に係るシール一体型ピストンの第一の形態を、油圧作動クラッチの一部と共に軸心Ｏを通る平面で切断して示す片側断面図である。1 is a half sectional view showing a first embodiment of a piston with an integrated seal according to the present invention by cutting along a plane passing through an axis O together with a part of a hydraulically operated clutch. 図１の要部拡大断面図である。It is a principal part expanded sectional view of FIG. 第一の形態における形状変更例を示す要部拡大断面図である。It is a principal part expanded sectional view which shows the example of a shape change in a 1st form. 従来のシール一体型ピストンを用いた油圧作動クラッチの概略構成を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 6 is a one-side cross-sectional view showing a schematic configuration of a hydraulically operated clutch using a conventional seal-integrated piston, cut along a plane passing through an axis O. 図４の一部を拡大した断面図である。It is sectional drawing to which a part of FIG. 4 was expanded.

符号の説明Explanation of symbols

１１０ クラッチシリンダ
１２０ シール一体型ピストン
１２１ ピストン本体
１２１ｅ 外周筒部
１２１ｆ クラッチ押圧部
１２１ｇ 円錐状段差面
１２２，１２３ シールリップ
１２４，１２５ ゴム膜
１３０ 多板クラッチ
１４０ 油圧室
２００ 金型 110 Clutch cylinder 120 Integrated piston piston
121 Piston body 121e Outer cylinder part
121f Clutch pressing part 121g Conical step surface
122,123 Seal lip
124,125 Rubber membrane
130 Multi-plate clutch 140 Hydraulic chamber 200 Mold

Claims (1)

クラッチシリンダ内に軸方向移動可能に配置されたピストン本体と、このピストン本体の外周筒部に一体に設けられ前記クラッチシリンダの内面に軸方向摺動可能に密接されるシールリップとを備え、前記ピストン本体の外周筒部の外周面に先端側へ向けて小径となり前記外周筒部の肉厚を減少させる円錐状段差面が形成され、前記ピストン本体の外周筒部の先端に、多板クラッチを押圧可能なクラッチ押圧部が前記円錐状段差面を介して突設され、前記シールリップの基部から前記ピストン本体の外周筒部の外周面を覆うように延びるゴム膜の端部が、前記円錐状段差面又はこの円錐状段差面の端部に位置することを特徴とするシール一体型ピストン。 A piston body disposed in the clutch cylinder so as to be movable in the axial direction; and a seal lip provided integrally with an outer peripheral cylindrical portion of the piston body and in close contact with the inner surface of the clutch cylinder so as to be slidable in the axial direction. A conical stepped surface is formed on the outer peripheral surface of the outer peripheral cylindrical portion of the piston main body, the diameter of which decreases toward the distal end, and reduces the thickness of the outer peripheral cylindrical portion. A pressable clutch pressing portion projects from the conical stepped surface, and an end portion of the rubber film extending from the base portion of the seal lip so as to cover the outer peripheral surface of the outer peripheral cylindrical portion of the piston body is the conical shape. A piston with an integrated seal, which is located at a stepped surface or an end of the conical stepped surface.
JP2007209354A 2007-08-10 2007-08-10 Integrated piston piston Active JP5182474B2 (en)

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WO2012024093A2 (en) * 2010-08-17 2012-02-23 Borgwarner Inc. Pneumatic clutch with improved friction member
US9739318B2 (en) 2015-05-20 2017-08-22 Federal-Mogul Llc Clutch piston assembly
JP7329360B2 (en) * 2019-05-10 2023-08-18 Nok株式会社 Piston seal for automatic transmission
US12038088B2 (en) * 2019-10-25 2024-07-16 Nok Corporation Sealing device

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JPS5779332A (en) * 1980-11-06 1982-05-18 Nissan Motor Co Ltd Clutch drum
US5558195A (en) * 1994-07-28 1996-09-24 Kuhlman Corporation Substantially rectangular cross section transmission spring
JPH09210088A (en) * 1996-01-29 1997-08-12 Nok Corp Sealing device
JP2903209B2 (en) * 1996-05-30 1999-06-07 三菱電線工業株式会社 Piston for automatic transmission
JP3308200B2 (en) * 1997-12-26 2002-07-29 三菱電線工業株式会社 Piston for automatic transmission
US6039160A (en) * 1998-08-31 2000-03-21 General Motors Corporation Friction torque transmitter with a one-way actuator
JP2004218821A (en) * 2002-11-19 2004-08-05 Nok Corp Sealing device
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JP2006138398A (en) * 2004-11-12 2006-06-01 Nok Corp Clutch piston
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